Means for effecting reciprocatory motion



March 9, 1948. P. R. HOOPES MEANS FOR EFFECTING RECIPROGATORY Filed Feb.20, 1945 3 Sheets-Sheet l INVENTOR:

W1 TNESSES w. w m R W m gjmiam/ozi March 9, 1948.

WI TN ESSES woo P. R. HOOPES MEANS FOR EFFECTING RECIPROCATORY FiledFeb. 20,1945

3 Sheets-Sheei 2 INVENTOR: Pen/rose Rfioo ves,

ATTORNEYS.

March 9, 1948. HOOPES 2,437,530

MEANS FOR EFFECTING RECIPROCATORY Filed Feb. 20, 1945 3 Sheets-Sheet 3WITNESSES INVENTOR:

PenmsefiHoqpes,

Chum/z ATTORNEYS.

Patented Mar. 9, i948 MEANS FOR EFFECTING RECIPROCATORY MOTION PenroseIt. Hoopes, Philadelphia, Pa, assignor to Super Speed Press Corporation,Bridgeton, N. J a corporation of Delaware Application February 20, 1945,Serial No. 578,843

5 Claims.

This invention relates to means useful in machines of various kinds forimparting motion to a member which is to be reciprocated. In connectionwith such means, it is the chief aim of my invention to make it possibleto vary the throw of the reciprocated element between zero and themaximum for which the means is designed, with maintenance of a perfectbalance in the parts in all positions of adjustment so that the machinesin which my invention is incorporated can be operated at much higherspeeds than heretofore with absence of vibration and with correspondingincrease in productive output.

One way in which the foregoing and other objects and advantages may bereadily realized in practice will appear from the following detaileddescription of the attached drawings, wherein Fig. 1 is a fragmentaryview in sectional elevation of a punching or stampin press convenientlyembodying the reciprocating means of myinvention.

Figs. 2 and 3 are detail sections on a larger scale taken as indicatedby the angled arrows IIII and III--III in Fig. 1, showing the recip-1igrcating means adjusted to impart the maximum Fig. 4 is a detailsectional view likewise on a larger scale taken as indicated by theangled arrows IV-IV in Fig. 1.

Figs. 5 and 6 are views like Fig. 4 showing the parts in differentpositions of adjustment.

Figs. '7, 8 and 9 are diagrammatic views, respectively corresponding toFigs. 4, 5 and 6.

With more detailed reference first more particularly to Fig. 1 of theseillustrations, the press therein shown for convenience of exemplifyingmy invention has a frame with spaced rigid standards or columns l and Hwhich are connected at the top by a bridging member l2. Disposed in thespace between the standards or columns. I 0 and II of the frame is thevertically reciprocative member l3 of the press which has the form of ayoke with side members l and I6 and a connecting cross member I! at thetop.

The adjustable means provided for reciprocating the yoke l3 inaccordance with my invention includes a rotary shaft with a journalportion I 8 at one end, and with an integrally-formed laterally-ofl'setcrank extension 19 at the other end. The journal portion l8 of the shaftis rotatively supported in a bearing 20 suitably mounted in the standardIII, while the crank extension I 9 is engaged and held within theeccentric bore of a bushing 2| which is rotative in a bearing 22 in thestandard I l in line with the main bearing 20. In the illustratedinstance, the shaft is driven through a clutch generally designated bythe numeral 23 by a fly wheel 2t having belt grooves at 25; and anautomatic brake comprehensively designated 26 is relied upon to stop theshaft upon disconnection of said clutch. The last described devices andother parts of the press except those about to be referred to, do notform any part of the present invention and do not therefore need furthermention.

Mounted on the crank extension [9 of the shaft with capacity forrotative adjustment thereon in a manner later on explained is a sleeve21. Ad jacent its ends, this sleeve 21 is formed withcontiguously-arranged integral eccentric enlargements 28, 29 and 23a,29a, of which the latter arediametrically opposed to and counterbalancethe former about the axis B of the crank portion IQ of. the shaft I8. Asshown, the eccentric enlargements 28 and 29 are centered on an axis Cand extend through bearings 30 and 3| in the side portions l5 and N5 ofthe reciprocated member, while the eccentric enlargements 23a. and 29aare centered on the shaft-bushing axis A. The sleeve 21 is moreoverformed at its very ends with integral, flanges 32 and 3'! which arecentered on the crank axis B. As further shown, the sleeve flange 32abuts an eccentric flange 33 integrallyformed medially of the driveshaft l8 and corn tered in the crank axis B. The shaft flange 33 is madewith a conical peripher for wedging ac tion with a surrounding clampring 34 and has a shouldered portion 33a which snugly fits into a recessin the contiguous face of the sleeve flange 32. The shaft flange 33 ismoreover provided with a circumferential series of tapped holes toreceive the shanks of headed screws 35 passed through screw holes in thesleeve flange 32. The other sleeve flange 31 in turn abuts a concentricconical flange 38 on the bushing 2|, the latter flange being providedwith a shouldered portion 2 la which snugly fits into a recess in thecontiguous face of the flange 38. A clamp ring 39 surrounding the flange38 is provided with a circumferential series of tapped holes forengagement by the shanks of headed screws 40 passed, as before stated,through the screw holes of the sleeve flange 31. Attention is directedto the fact that the eccentricity of the enlarged portions 28, 29 of thesleeve 21 relative to the crank 19 is equal to the eccentricity of saidcrank extension [9 relative to the shaft; that is to say, the axis C is01iset from the axis B by the same distance as the axis B is offset fromthe axis A. Secured by screws 4| and 42 to the shaft and bushing flanges33 and 38 respectively are weighted annular elements 43 and 44 whichcounterbalance said flanges and the crank portion IQ of the shaft 18. Asshown the elements 43 and 44 are centered on the shaft-bushing axis'Aand have openings centered on the crank axis B to snugly receive thesleeve flanges 32 and 31.

With the sleeve 21 set as shown in Figs. 1-4, it will be seen that theeccentricity f the portions 28 and 29 of the sleeve 21 is added to thatof the crank I9 so that maximum movement is imparted to the reciprocatedelement l3, the effective crank radius being as indicated by the arrow Rin Fig. 7. To change the adjustment, the screws 35 and 40 are backed offto relieve the clamp rings crank axis; a bushing coaxial with thejournal portion of the drive shaft, said bushing having an eccentricbore in which the end of the crank extension is engaged, and aneccentric flange centered on the crank axis; bearings respectively forthe journal portion of the shaft and the bushing; a sleeve mounted withcapacity for rotative adjustment about the crank between the shaftflange and the bushing, said sleeve having an eccentric enlargement foractuating a member which is to be reciprocated, and end flanges centeredon the crank axis and respectively abutting the shaft and bushingflanges; clamp means operative to connect the sleeve flanges with theshaft and bushing flanges to secure the sleeve in adjusted positions;and means whereby the sleeve 34 and. 39 so that the sleeve 21 may berotated in either direction about the crank I9 until the desiredadjustment is had, whereupon said screws are re-tightened to hold suchadjustment. The adjustment may be effected by means of a spanner wrenchinserted into holes provided for that purpose in flanges 36 and 31. Byturning the sleeve 2! through 180 from the position of Figs. 1, 3, 4 and7 to the position of Figs. 5 and 8, the axis C is brought intocoincidence with the shaftbushing axis A with the result that theeffective crank radius will be zero. Again, by turning the sleeve 21through a smaller angle as exemplified in Figs. 6 and 9, the effectivecrank radius will be shortened to the distance R and the movement of themember [5 correspondingly reduced.

Since, by reason of the described construction, the sleeve 21 isperfectly balanced about the crank axis B by the counterweighting at 28cand 29a, and the sleeve mass together with the crank extension I9 isperfectly balanced about the shaft axis A by the counterweighting at 43and 44, it follows that the rotation of the drive shaft will beunattended by vibration for positions of adjustment of the crank throw.Accordingly machines in which the reciprocating means of my inventionare employed can be safely operated at much higher speeds thanheretofore possible and their output in turn correspondingly increased.Moreover due to the coaction between the shouldered portions 33a and 38aof the shaft and bushing flanges 33 and 38 and the recesses in thecollar flanges 32 and 31, it will be seen that the crank extension l9 ofsaid shaft and the sleeve 21 are effectively stiffened to withstand anyforces tending to flex or bend them incident to high speed operation ofthe machines.

Having thus described my invention, I claim:

1. Means for effecting reciprocatory motion including anintegrally-formed drive shaft element with a journal portion at one end,a laterallyoffset crank extension at the other end, and amedially-located eccentric flange centered on the is dynamicallybalanced about the crank axis, and whereby the crank and the sleeve aredynamically balanced about the shaft-bushing axis for allrotatively-adjuste'd positions of said sleeve.

2. The invention definedin claim 1, wherein the displacement of theeccentric portion of the sleeve relative to the crank axis is equal tothe displacement of said crank axis relative to the shaft-bushing axis.

3. The invention defined in claim 1, wherein the drive shaft and thebushing flanges have shouldered portions concentric with the crank axiswhich snugly fit into recesses in the contiguous faces of thecorresponding sleeve flanges.

4. The invention defined in claim 1, wherein the peripheries of theshaft and bushing flanges are conical; wherein correspondingly boredclamp rings fit over said flanges; and wherein the shanks of headedscrews are passed through screw holes in the sleeve flanges andthreadedly engage tapped'holes in said clamp rings.

5. The invention defined in claim 1, wherein the balancing means includean integral eccentric portion on the sleeve disposed diametricallyopposite the eccentric enlargement for actuating the reciprocatedmember, and counterweight e1e-1 merits centered on a shaft axis andsecured'to the shaft and the bushing flanges, said elements havingcircular openings centered on the crank axis and fitting over saidsleeve flanges.

PENROSE R. HOOPES.

REFERENCES CITED The following references are of record in the file ofthis patent:

UNITED STATES PATENTS Number Name Date 1,137,877 Manly et a1. May 4,1915 FOREIGN PATENTS Number Country Date 115,219 Great Britain May2,1918

